CN104121721B - Single-and-double-stage switchable heat pump - Google Patents

Single-and-double-stage switchable heat pump Download PDF

Info

Publication number
CN104121721B
CN104121721B CN201410314899.4A CN201410314899A CN104121721B CN 104121721 B CN104121721 B CN 104121721B CN 201410314899 A CN201410314899 A CN 201410314899A CN 104121721 B CN104121721 B CN 104121721B
Authority
CN
China
Prior art keywords
pressure
heat exchanger
low
compressor
heat pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201410314899.4A
Other languages
Chinese (zh)
Other versions
CN104121721A (en
Inventor
刘远辉
王超毅
高翔
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Guangdong PHNIX Eco Energy Solution Ltd
Original Assignee
Guangdong PHNIX Eco Energy Solution Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Guangdong PHNIX Eco Energy Solution Ltd filed Critical Guangdong PHNIX Eco Energy Solution Ltd
Priority to CN201410314899.4A priority Critical patent/CN104121721B/en
Publication of CN104121721A publication Critical patent/CN104121721A/en
Application granted granted Critical
Publication of CN104121721B publication Critical patent/CN104121721B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

The invention discloses a single-and-double-stage switchable heat pump and belongs to the field of heat pump systems. The heat pump comprises a low-pressure system, a high-pressure system and a main heat exchanger connected in parallel between the low-pressure system and the high-pressure system. A first compressor and a first heat exchanger are arranged in the low-pressure system and connected in series with a left side pipeline of the main heat exchanger. A second compressor and a second heat exchanger are arranged in the high-pressure system and connected in series with a right side pipeline of the main heat exchanger. According to the single-and-double-stage switchable heat pump, the low-pressure system and the high-pressure system are formed by single-stage heat pump bodies and connected in parallel through the main heat exchanger, single-stage heat pump refrigerating/heating circulation can be performed as long as the first compressor in the low-pressure system is independently turned on, and cascade heat pump heating operation can be achieved as long as the second compressor is firstly turned on and the first compressor is turned on afterwards. The heat pump system can be freely switched between the single-stage heat pump mode and the cascade heat pump mode, and therefore the purposes of fully utilizing the advantages of both the modes and effectively saving energy and reducing emissions are achieved.

Description

A kind of single switchable heat pump of twin-stage
Technical field
The present invention relates to a kind of heat pump, particularly relate to a kind of single switchable heat pump of twin-stage.
Background technology
Although common cascade type heat pump well meets the demand of low-temperature heating and high-temperature-hot-water, but when unit refrigerating operaton, its refrigerating efficiency is the highest, can only meet simple defrosting, and cannot meet the demand of highly effective refrigeration.And, common cascade type heat pump is under ambient temperature is in the high environment of 0 DEG C~15 DEG C during heating, and its heating efficiency is the highest.And single-stage heat pump has the advantage that refrigerating operaton efficiency is high and epipodium temperature heating heating efficiency is high, therefore need to design a heat pump that can freely switch single-stage heat pump and cascade type heat pump operation, year round cooling and the demand heated can be met.
Summary of the invention
For solving the problems referred to above, the present invention provides a kind of changeable heat pump of single twin-stage that can freely switch to single-stage operation of heat pump or cascade type heat pump operation.
The technical solution adopted for the present invention to solve the technical problems is:
A kind of single switchable heat pump of twin-stage, including low-pressure system and high-pressure system and the main heat exchanger being connected in parallel between low-pressure system and high-pressure system, low-pressure system is provided with the first compressor and the First Heat Exchanger of left side placed in series with main heat exchanger, high-pressure system is provided with main heat exchanger on the right side of the second compressor of placed in series and the second heat exchanger.
It is further used as the improvement of technical solution of the present invention, low-pressure system is additionally provided with the low-pressure end heat exchanger being series between the first compressor and main heat exchanger by cross valve.
It is further used as the improvement of technical solution of the present invention, low-pressure system is additionally provided with the low-pressure end heat exchanger in parallel with main heat exchanger.
Being further used as the improvement of technical solution of the present invention, connecting between the input of First Heat Exchanger and the outfan of the first compressor and main heat exchanger has the first economizer.
Being further used as the improvement of technical solution of the present invention, connecting between the input of main heat exchanger and the outfan of the second compressor and the second heat exchanger has the second economizer.
It is further used as the improvement of technical solution of the present invention, with be additionally provided with threeth heat exchange pipeline in parallel with two heat exchange pipelines in main heat exchanger in main heat exchanger, being connected with the two ends of the 3rd heat exchange pipeline is provided with inlet side and the water-circulating pipe of outlet side being respectively connecting to the second heat exchanger by three-way valve.
Being further used as the improvement of technical solution of the present invention, be connected the pulsating pump being provided with water-circulating pipe and be arranged on water-circulating pipe with low-pressure end heat exchanger.
It is further used as the improvement of technical solution of the present invention, is connected with low-pressure end heat exchanger and is provided with inlet side and the water-circulating pipe of outlet side being respectively connecting to the second heat exchanger by three-way valve.
Beneficial effects of the present invention: low-pressure system and high-pressure system that single-stage heat pump is consisted of by this single switchable heat pump of twin-stage main heat exchanger are together in parallel, individually open the first compressor in low-pressure system and can carry out single-stage heat pump refrigerating/heat circulation, first open the second compressor, later on first compressor can realize the heating operation of cascade type heat pump, this heat pump freely can switch in single-stage heat pump and cascade type heat pump pattern, reach to make full use of each pattern advantage, and the purpose of effectively energy-saving and emission-reduction.
Accompanying drawing explanation
The invention will be further described below in conjunction with the accompanying drawings:
Fig. 1 is first embodiment of the invention overall structure schematic diagram;
Fig. 2 is second embodiment of the invention overall structure schematic diagram;
Fig. 3 is third embodiment of the invention overall structure schematic diagram.
Detailed description of the invention
With reference to Fig. 1~Fig. 3, the present invention is a kind of single switchable heat pump of twin-stage, including low-pressure system 1 and high-pressure system 2 and the main heat exchanger 3 being connected in parallel between low-pressure system 1 and high-pressure system 2, low-pressure system 1 is provided with the first compressor 11 and the First Heat Exchanger 12 of left side placed in series with main heat exchanger 3, high-pressure system 2 is provided with main heat exchanger 3 on the right side of the second compressor 21 and the second heat exchanger 22 of placed in series.
Low-pressure system 1 and high-pressure system 2 that single-stage heat pump is consisted of by this single switchable heat pump of twin-stage main heat exchanger 3 are together in parallel, individually open the first compressor 11 in low-pressure system 1 and can carry out single-stage heat pump refrigerating/heat circulation, first open the second compressor 21, later on first compressor 11 can realize the heating operation of cascade type heat pump, this heat pump freely can switch in single-stage heat pump and cascade type heat pump pattern, reach to make full use of each pattern a little, and the purpose of effectively energy-saving and emission-reduction.
As the preferred embodiment of the present invention, low-pressure system 1 is additionally provided with and is series at the low-pressure end heat exchanger 14 between the first compressor 11 and main heat exchanger 3 by cross valve 13.
As the preferred embodiment of the present invention, be connected the pulsating pump 5 being provided with water-circulating pipe 4 and be arranged on water-circulating pipe 4 with low-pressure end heat exchanger 14.
As the preferred embodiment of the present invention, connect between the input of First Heat Exchanger 12 and the outfan of the first compressor 11 and main heat exchanger 3 and have the first economizer 15.
As the preferred embodiment of the present invention, connect between the input of main heat exchanger 3 and the outfan of the second compressor 21 and the second heat exchanger 22 and have the second economizer 23.
In the first embodiment, individually open the first compressor 11, the single-stage operation of heat pump under this state can be realized.Under this state, the refrigerant gas of High Temperature High Pressure discharged by first compressor 11, high-temperature high-pressure refrigerant gas flows to from the D mouth of cross valve 13, flow out from the C mouth of cross valve 13, enter into the refrigerant liquid becoming cryogenic high pressure after condensing in low-pressure end heat exchanger 14, the cryogenic high pressure refrigerant liquid point two-way flowing after main heat exchanger 3 flowed out from low-pressure end heat exchanger 14, a road is major loop, and another road is auxiliary loop.The refrigerant liquid of major loop enters the first economizer 15, the refrigerant liquid in auxiliary loop becomes the gas-liquid mixture of low pressure after electric expansion valve blood pressure lowering, also the first economizer 15 is simultaneously entered, after two-way cold-producing medium produces heat exchange in the first economizer 15, the cold-producing medium draw heat in auxiliary loop is sucked by the auxilairy air intake of the first compressor 11 after becoming gas.The cold-producing medium of main road flows out from the supercool outlet of the first economizer 15, after becoming subcooled liquid, in flow throttling device after reducing pressure by regulating flow, enters in First Heat Exchanger 12 and is evaporated.Low-temperature low-pressure refrigerant gas after completing evaporation sequentially passes through the E mouth of cross valve 13, S mouth, enters the first gas-liquid separator 16, then flows out from the first gas-liquid separator 16, returns to the first compressor 11 from the gas returning port of the first compressor 11.Now, extraneous tap water carries out heat exchange with high temperature refrigerant in pulsating pump 5 enters into low-pressure end heat exchanger 14, and after heat exchange, hot water flows out through the outlet of low-pressure end heat exchanger 14, it is provided that heating and hot water.Commutated refrigerating operaton by cross valve 13, it is possible to realize highly effective refrigeration simultaneously.
When needing to use Cascade type heat pump system to heat, first open the second compressor 21, be then turned on the first compressor 11.In high-pressure system 2 side, the refrigerant gas of High Temperature High Pressure discharged by second compressor 21, high-temperature high-pressure refrigerant gas enters in the second heat exchanger 22, cryogenic high pressure refrigerant liquid is become after carrying out heat exchange with the cold water simultaneously entered in the second heat exchanger 22, the cryogenic high pressure refrigerant liquid flowed out from the second heat exchanger 22 divides two-way to flow, one tunnel is major loop, and another road is auxiliary loop.The refrigerant liquid of major loop enters the second economizer 23, the refrigerant liquid in auxiliary loop becomes the gas-liquid mixture of low pressure after electric expansion valve blood pressure lowering, also the second economizer 23 is simultaneously entered, after two-way cold-producing medium produces heat exchange in the second economizer 23, the cold-producing medium draw heat in auxiliary loop is sucked by the auxilairy air intake of the second compressor 21 after becoming gas.The cold-producing medium of main road flows out from the supercool outlet of the second economizer 23, after becoming subcooled liquid, and reducing pressure by regulating flow in flow throttling device, then flow in main heat exchanger 3.The refrigerant liquid of low-temp low-pressure absorbs main heat exchanger 3 in main heat exchanger 3 and condenses the heat discharged in low-pressure system for evaporating, low-temperature low-pressure refrigerant gas after completing evaporation enters the second gas-liquid separator 24, flow out from the second gas-liquid separator 24 again, return to the second compressor 21 from the gas returning port of the second compressor 21.Now, extraneous tap water is entered by the water inlet of the second heat exchanger 22 and carries out heat exchange with high temperature refrigerant, and the hot water after heat exchange is flowed out by the outlet of the second heat exchanger 22 again, it is provided that high-temperature-hot-water.
When using cascade type heat pump, in low-pressure system 1 side, the refrigerant gas of High Temperature High Pressure discharged by first compressor 11, high-temperature high-pressure refrigerant gas flows to from the D mouth of cross valve 13, flowing out from the C mouth of cross valve 13, entered into the refrigerant liquid becoming cryogenic high pressure after condensing in main heat exchanger 3 by low-pressure end heat exchanger 14, the cryogenic high pressure refrigerant liquid flowed out from main heat exchanger 3 divides two-way to flow, one tunnel is major loop, and another road is auxiliary loop.The refrigerant liquid of major loop enters the first economizer 15, the refrigerant liquid in auxiliary loop becomes the gas-liquid mixture of low pressure after electric expansion valve blood pressure lowering, also the first economizer 15 is simultaneously entered, after two-way cold-producing medium produces heat exchange in the first economizer 15, the cold-producing medium draw heat in auxiliary loop is sucked by the auxilairy air intake of the first compressor 11 after becoming gas.The cold-producing medium of main road flows out from the supercool outlet of the first economizer 15, after becoming subcooled liquid, in flow throttling device after reducing pressure by regulating flow, enters in First Heat Exchanger 12 and is evaporated.Low-temperature low-pressure refrigerant gas after completing evaporation sequentially passes through the E mouth of cross valve 13, S mouth, enters the first gas-liquid separator 16, then flows out from the first gas-liquid separator 16, returns to the first compressor 11 from the gas returning port of the first compressor 11.
As the preferred embodiment of the present invention, low-pressure system 1 is additionally provided with the low-pressure end heat exchanger 14 in parallel with main heat exchanger 3.
As the preferred embodiment of the present invention, it is connected with low-pressure end heat exchanger 14 and is provided with inlet side and the water-circulating pipe 4 of outlet side being respectively connecting to the second heat exchanger 22 by three-way valve.
As the preferred embodiment of the present invention, connect between the input of First Heat Exchanger 12 and the outfan of the first compressor 11 and main heat exchanger 3 and have the first economizer 15.
As the preferred embodiment of the present invention, connect between the input of main heat exchanger 3 and the outfan of the second compressor 21 and the second heat exchanger 22 and have the second economizer 23.
In a second embodiment, low-pressure end heat exchanger 14 is connected in parallel to each other with main heat exchanger 3, and is provided with the first electromagnetism two-port valve 17 and the second electromagnetism two-port valve 18 at the air inlet of low-pressure end heat exchanger 14 and the air inlet of main heat exchanger 3 respectively.Under this state, individually open the first compressor 11, single-stage operation of heat pump can be realized.During use, first electromagnetism two-port valve 17 is opened, second electromagnetism two-port valve 18 cuts out, the refrigerant gas of High Temperature High Pressure discharged by first compressor 11, and high-temperature high-pressure refrigerant gas flows to from the D mouth of cross valve 13, flows out from the C mouth of cross valve 13, enter the refrigerant liquid becoming cryogenic high pressure after condensing in low-pressure end heat exchanger 14, the cryogenic high pressure refrigerant liquid flowed out from low-pressure end heat exchanger 14 divides two-way to flow, and a road is major loop, and another road is auxiliary loop.The refrigerant liquid of major loop enters the first economizer 15, the refrigerant liquid in auxiliary loop becomes the gas-liquid mixture of low pressure after electric expansion valve blood pressure lowering, also the first economizer 15 is simultaneously entered, after two-way cold-producing medium produces heat exchange in the first economizer 15, the cold-producing medium draw heat in auxiliary loop is sucked by the auxilairy air intake of the first compressor 11 after becoming gas.The cold-producing medium of main road flows out from the supercool outlet of the first economizer 15, after becoming subcooled liquid, in flow throttling device after reducing pressure by regulating flow, enters in First Heat Exchanger 12 and is evaporated.Low-temperature low-pressure refrigerant gas after completing evaporation sequentially passes through the E mouth of cross valve 13, S mouth, enters the first gas-liquid separator, then flows out from the first gas-liquid separator 16, returns to the first compressor 11 from the gas returning port of the first compressor 11.Now, extraneous tap water, through pulsating pump 5, is entered in low-pressure end heat exchanger 14 by T-way water valve and carries out heat exchange with high temperature refrigerant, and after heat exchange, hot water is flowed out by T-way water valve again, it is provided that heating and hot water.Commutated refrigerating operaton by cross valve 13, it is possible to realize highly effective refrigeration simultaneously.
When using cascade type heat pump, in high-pressure system 2 side, the refrigerant gas of High Temperature High Pressure discharged by second compressor 21, high-temperature high-pressure refrigerant gas enters in the second heat exchanger 22, cryogenic high pressure refrigerant liquid is become after carrying out heat exchange with the cold water simultaneously entered in the second heat exchanger 22, the cryogenic high pressure refrigerant liquid flowed out from the second heat exchanger 22 divides two-way to flow, and a road is major loop, and another road is auxiliary loop.The refrigerant liquid of major loop enters the second economizer 23, the refrigerant liquid in auxiliary loop becomes the gas-liquid mixture of low pressure after electric expansion valve blood pressure lowering, also the second economizer 23 is simultaneously entered, after two-way cold-producing medium produces heat exchange in the second economizer 23, the cold-producing medium draw heat in auxiliary loop is sucked by the auxilairy air intake of the second compressor 21 after becoming gas.The cold-producing medium of main road flows out from the supercool outlet of the second economizer 23, after becoming subcooled liquid, and reducing pressure by regulating flow in flow throttling device, then flow in main heat exchanger 3.The refrigerant liquid of low-temp low-pressure absorbs main heat exchanger 3 in main heat exchanger 3 and condenses the heat discharged in low-pressure system for evaporating, low-temperature low-pressure refrigerant gas after completing evaporation sequentially passes through the E mouth of cross valve 13, S mouth, enter the second gas-liquid separator 24, flow out from the second gas-liquid separator 24 again, return to the second compressor 21 from the gas returning port of the second compressor 21.Now, extraneous tap water enters the second heat exchanger 22 by T-way water valve and carries out heat exchange with high temperature refrigerant, and the hot water after heat exchange is flowed out by T-way water valve again, it is provided that high-temperature-hot-water.
Now, in low-pressure system 1 side, the refrigerant gas of High Temperature High Pressure discharged by first compressor 11, high-temperature high-pressure refrigerant gas flows to from the D mouth of cross valve 13, flowing out from the C mouth of cross valve 13, enter into the refrigerant liquid becoming cryogenic high pressure after condensing in main heat exchanger 3, the cryogenic high pressure refrigerant liquid flowed out from main heat exchanger 3 divides two-way to flow, one tunnel is major loop, and another road is auxiliary loop.The refrigerant liquid of major loop enters the first economizer 15, the refrigerant liquid in auxiliary loop becomes the gas-liquid mixture of low pressure after electric expansion valve blood pressure lowering, also the first economizer 15 is simultaneously entered, after two-way cold-producing medium produces heat exchange in the first economizer 15, the cold-producing medium draw heat in auxiliary loop is sucked by the auxilairy air intake of the first compressor 11 after becoming gas.The cold-producing medium of main road flows out from the supercool outlet of the first economizer 15, after becoming subcooled liquid, in flow throttling device after reducing pressure by regulating flow, enters in First Heat Exchanger 12 and is evaporated.Low-temperature low-pressure refrigerant gas after completing evaporation sequentially passes through the E mouth of cross valve 13, S mouth, enters the first gas-liquid separator 16, then flows out from the first gas-liquid separator 16, returns to the first compressor 11 from the gas returning port of the first compressor 11.
As the preferred embodiment of the present invention, in the third embodiment, with be additionally provided with threeth heat exchange pipeline in parallel with two heat exchange pipelines in main heat exchanger 3 in main heat exchanger 3, be connected with the two ends of the 3rd heat exchange pipeline and be provided with inlet side and the water-circulating pipe 4 of outlet side being respectively connecting to the second heat exchanger 22 by three-way valve.
In 3rd embodiment, dispense the setting of low-pressure end heat exchanger 14.When carrying out single-stage operation of heat pump refrigeration, directly carry out heat exchange realization by main heat exchanger 3 inside left heat exchanger tube and the 3rd heat exchange pipeline and heat.Commutated refrigerating operaton by cross valve 13, it is possible to realize highly effective refrigeration simultaneously.
And when using Cascade type heat pump system, in high-pressure system 2 side, the refrigerant gas of High Temperature High Pressure discharged by second compressor 21, high-temperature high-pressure refrigerant gas enters in the second heat exchanger 22, cryogenic high pressure refrigerant liquid is become after carrying out heat exchange with the cold water simultaneously entered in the second heat exchanger 22, the cryogenic high pressure refrigerant liquid flowed out from the second heat exchanger 22 divides two-way to flow, and a road is major loop, and another road is auxiliary loop.The refrigerant liquid of major loop enters the second economizer 23, the refrigerant liquid in auxiliary loop becomes the gas-liquid mixture of low pressure after electric expansion valve blood pressure lowering, also the second economizer 23 is simultaneously entered, after two-way cold-producing medium produces heat exchange in the second economizer 23, the cold-producing medium draw heat in auxiliary loop is sucked by the auxilairy air intake of the second compressor 21 after becoming gas.The cold-producing medium of main road flows out from the supercool outlet of the second economizer 23, after becoming subcooled liquid, and reducing pressure by regulating flow in flow throttling device, enter back on the right side of main heat exchanger 3 in heat exchange pipeline.The refrigerant liquid of low-temp low-pressure absorbs heat that main heat exchanger 3 inside left heat exchange pipeline discharged for evaporating, low-temperature low-pressure refrigerant gas after completing evaporation sequentially passes through the E mouth of cross valve 13, S mouth, enter the second gas-liquid separator 24, flow out from the second gas-liquid separator 24 again, return to the second compressor 21 from the gas returning port of the second compressor 21.Now, extraneous tap water enters the second heat exchanger 22 by T-way water valve and carries out heat exchange with high temperature refrigerant, and the hot water after heat exchange is flowed out by T-way water valve again, it is provided that high-temperature-hot-water.
Now, in low-pressure system 1 side, the refrigerant gas of High Temperature High Pressure discharged by first compressor 11, high-temperature high-pressure refrigerant gas flows to from the D mouth of cross valve 13, flowing out from the C mouth of cross valve 13, enter into the refrigerant liquid becoming cryogenic high pressure after condensing in main heat exchanger 3 inside left heat exchanger channels, the cryogenic high pressure refrigerant liquid flowed out from low-pressure end heat exchanger 14 divides two-way to flow, one tunnel is major loop, and another road is auxiliary loop.The refrigerant liquid of major loop enters the first economizer 15, the refrigerant liquid in auxiliary loop becomes the gas-liquid mixture of low pressure after electric expansion valve blood pressure lowering, also the first economizer 15 is simultaneously entered, after two-way cold-producing medium produces heat exchange in the first economizer 15, the cold-producing medium draw heat in auxiliary loop is sucked by the auxilairy air intake of the first compressor 11 after becoming gas.The cold-producing medium of main road flows out from the supercool outlet of the first economizer 15, after becoming subcooled liquid, in flow throttling device after reducing pressure by regulating flow, enters in First Heat Exchanger 12 and is evaporated.Low-temperature low-pressure refrigerant gas after completing evaporation sequentially passes through the E mouth of cross valve 14, S mouth, enters the first gas-liquid separator 16, then flows out from the first gas-liquid separator 16, returns to the first compressor 11 from the gas returning port of the first compressor 11.
Single-stage heat pump is incorporated in cascade high-temperature heat pump system by this system, the advantage high according to single-stage heat pump refrigerating operational efficiency and cascade high-temperature heat pump ultralow temperature heating effect is good, the advantage that can produce high-temperature-hot-water rationally switches use so that the function such as unit can realize freezing, heats, domestic hot-water, high-temperature-hot-water.
When unit heating under the high environment that ambient temperature is in 0 DEG C-15 DEG C, unit is switched to the work of single-stage heat pump, takes full advantage of the advantage that single-stage heat pump efficiently can heat in epipodium temperature, compensate for the deficiency that cascade type heat pump epipodium temperature heating efficiency is low.
In the first and second embodiment, single-stage heat pump is made up of plus low-pressure end heat exchanger 14 low-pressure system 1, and in the third embodiment, single-stage heat pump is exactly low-pressure system 1, and input cost is the highest.Major part has only to open single-stage operation of heat pump season, is equivalent to major part and has only to individually open low-pressure system operation season, just can meet the demand of refrigeration, heating, domestic hot-water, thus save the energy.
During Defrost operation, also have only to out low-pressure system 1 and individually defrost, it is not necessary to open high-pressure system 2 and defrost, it is achieved that one-level defrost.Improve unit efficiency.
Certainly, the invention is not limited to above-mentioned embodiment, those of ordinary skill in the art also can make equivalent variations or replacement on the premise of spirit of the present invention, and modification or the replacement of these equivalents are all contained in the application claim limited range.

Claims (6)

  1. null1. the switchable heat pump of single twin-stage,It is characterized in that: include low-pressure system (1) and high-pressure system (2) and the main heat exchanger (3) being connected in parallel between described low-pressure system (1) and high-pressure system (2),Described low-pressure system (1) is provided with the first compressor (11) with the left side placed in series of main heat exchanger (3) and First Heat Exchanger (12),Described high-pressure system (2) is provided with the second compressor (21) with main heat exchanger (3) right side placed in series and the second heat exchanger (22),Described low-pressure system (1) is additionally provided with low-pressure end heat exchanger (14) or threeth heat exchange pipeline in parallel with two heat exchange pipelines in main heat exchanger (3),Described low-pressure end heat exchanger (14) is series between the first compressor (11) and main heat exchanger (3) by cross valve (13),Or described low-pressure end heat exchanger (14) is arranged in parallel with main heat exchanger (3).
  2. The switchable heat pump of single twin-stage the most according to claim 1, it is characterised in that: connect between the input of described First Heat Exchanger (12) and the outfan of the first compressor (11) and main heat exchanger (3) and have the first economizer (15).
  3. The switchable heat pump of single twin-stage the most according to claim 1 and 2, it is characterised in that: connect between the input of described main heat exchanger (3) and the outfan of the second compressor (21) and the second heat exchanger (22) and have the second economizer (23).
  4. The switchable heat pump of single twin-stage the most according to claim 1, it is characterised in that: it is connected with the two ends of described 3rd heat exchange pipeline and is provided with inlet side and the water-circulating pipe (4) of outlet side being respectively connecting to the second heat exchanger (22) by three-way valve.
  5. The switchable heat pump of single twin-stage the most according to claim 4, it is characterised in that: be connected the pulsating pump (5) being provided with water-circulating pipe (4) and be arranged on described water-circulating pipe (4) with described low-pressure end heat exchanger (14).
  6. The switchable heat pump of single twin-stage the most according to claim 5, it is characterised in that: it is connected with described low-pressure end heat exchanger (14) and is provided with inlet side and the water-circulating pipe (4) of outlet side being respectively connecting to the second heat exchanger (22) by three-way valve.
CN201410314899.4A 2014-07-02 2014-07-02 Single-and-double-stage switchable heat pump Active CN104121721B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201410314899.4A CN104121721B (en) 2014-07-02 2014-07-02 Single-and-double-stage switchable heat pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201410314899.4A CN104121721B (en) 2014-07-02 2014-07-02 Single-and-double-stage switchable heat pump

Publications (2)

Publication Number Publication Date
CN104121721A CN104121721A (en) 2014-10-29
CN104121721B true CN104121721B (en) 2017-01-11

Family

ID=51767243

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201410314899.4A Active CN104121721B (en) 2014-07-02 2014-07-02 Single-and-double-stage switchable heat pump

Country Status (1)

Country Link
CN (1) CN104121721B (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105937822A (en) * 2016-06-21 2016-09-14 广东芬尼克兹节能设备有限公司 Cascade type high-temperature heat pump with high defrosting performance and control method of cascade type high-temperature heat pump

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005257231A (en) * 2004-03-15 2005-09-22 Fujitsu General Ltd Heat pump hot water supply air conditioner
CN1757991A (en) * 2004-10-05 2006-04-12 Lg电子株式会社 Air-conditioner with a dual-refrigerant circuit
CN2906484Y (en) * 2006-03-28 2007-05-30 王全龄 Highly-efficient heating type heat pump type air conditioner especially suitable for use in low temperature condition
JP2012107836A (en) * 2010-11-19 2012-06-07 Hitachi Appliances Inc Binary refrigeration cycle apparatus
CN103307805A (en) * 2013-06-14 2013-09-18 上海海立睿能环境技术有限公司 Trigeneration heat pump system
CN203964449U (en) * 2014-07-02 2014-11-26 广东芬尼克兹节能设备有限公司 The switchable heat pump of a kind of single twin-stage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005257231A (en) * 2004-03-15 2005-09-22 Fujitsu General Ltd Heat pump hot water supply air conditioner
CN1757991A (en) * 2004-10-05 2006-04-12 Lg电子株式会社 Air-conditioner with a dual-refrigerant circuit
CN2906484Y (en) * 2006-03-28 2007-05-30 王全龄 Highly-efficient heating type heat pump type air conditioner especially suitable for use in low temperature condition
JP2012107836A (en) * 2010-11-19 2012-06-07 Hitachi Appliances Inc Binary refrigeration cycle apparatus
CN103307805A (en) * 2013-06-14 2013-09-18 上海海立睿能环境技术有限公司 Trigeneration heat pump system
CN203964449U (en) * 2014-07-02 2014-11-26 广东芬尼克兹节能设备有限公司 The switchable heat pump of a kind of single twin-stage

Also Published As

Publication number Publication date
CN104121721A (en) 2014-10-29

Similar Documents

Publication Publication Date Title
WO2019128516A1 (en) Air conditioner system
CN104061705B (en) Two-stage Compression air-conditioning system and its control method
US9885504B2 (en) Heat pump with water heating
CN105020924A (en) Air source enhanced vapor injection heat pump system
CN102645060A (en) Multi-split air conditioning system
WO2020073481A1 (en) Air conditioning system
CN203964449U (en) The switchable heat pump of a kind of single twin-stage
CN104833152A (en) Liquid impact preventing air conditioner defrosting system
CN102183104B (en) Indirect-expanding solar assisted multifunctional heat pump system
CN104075477A (en) Cascade high-temperature heat pump
KR101401909B1 (en) Heat pump chiller system by non-frosting continuous operating the heat exchanger and Defrost method
CN108061403A (en) A kind of two-way self-cascade heat pump system
CN104236164A (en) Ultra-high temperature cascade water source heat pump system
WO2019029233A1 (en) Air conditioning system and air conditioner having the same
CN104121721B (en) Single-and-double-stage switchable heat pump
CN108988109A (en) Dual temperature water cooling unit for laser
CN109059335A (en) A kind of low-temperature air source heat pump unit
CN202521952U (en) Ultralow temperature air source heat pump with double throttling devices
CN201652987U (en) Novel air conditioning system with cold and hot drinking water supply functions
CN201583048U (en) Heat pump water heater
CN203785316U (en) Air source heat pump unit
KR101461519B1 (en) Duality Cold Cycle Heat pump system of Control method
CN105258389A (en) Compensation type dual-source heat pump cold and hot water unit
CN104713264A (en) Air source heat pump set
CN205980489U (en) Energy -saving hot vapour defrosting system of air -source heat bump water heater

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant